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US6533065B2 - Noise silencer and method for use with an ultrasonic meter - Google Patents

Noise silencer and method for use with an ultrasonic meter Download PDF

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Publication number
US6533065B2
US6533065B2 US09/740,427 US74042700A US6533065B2 US 6533065 B2 US6533065 B2 US 6533065B2 US 74042700 A US74042700 A US 74042700A US 6533065 B2 US6533065 B2 US 6533065B2
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silencer
baffles
noise
ultrasonic
length
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US20030034202A1 (en
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Klaus Joachim Zanker
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Daniel Industries Inc
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Daniel Industries Inc
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Assigned to DANIEL INDUSTRIES, INC. reassignment DANIEL INDUSTRIES, INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ZANKER, KLAUS JOACHIM
Priority to EP01310488A priority patent/EP1217339A3/fr
Priority to CA002365051A priority patent/CA2365051A1/fr
Priority to MXPA01013102A priority patent/MXPA01013102A/es
Priority to RU2001134205/28A priority patent/RU2001134205A/ru
Publication of US20030034202A1 publication Critical patent/US20030034202A1/en
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    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01F—MEASURING VOLUME, VOLUME FLOW, MASS FLOW OR LIQUID LEVEL; METERING BY VOLUME
    • G01F1/00—Measuring the volume flow or mass flow of fluid or fluent solid material wherein the fluid passes through a meter in a continuous flow
    • G01F1/66—Measuring the volume flow or mass flow of fluid or fluent solid material wherein the fluid passes through a meter in a continuous flow by measuring frequency, phase shift or propagation time of electromagnetic or other waves, e.g. using ultrasonic flowmeters
    • G01F1/662—Constructional details
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01F—MEASURING VOLUME, VOLUME FLOW, MASS FLOW OR LIQUID LEVEL; METERING BY VOLUME
    • G01F15/00—Details of, or accessories for, apparatus of groups G01F1/00 - G01F13/00 insofar as such details or appliances are not adapted to particular types of such apparatus

Definitions

  • the present invention relates generally to a silencer and method for use with an ultrasonic meter that reduces noise in the ultrasonic range of frequencies generated by other equipment in the flow stream. More particularly, the invention relates to a silencer and method for use with an ultrasonic meter that is capable of reducing ultrasonic noise under high-pressure operating conditions. Still more particularly, the invention relates to a silencer and method for use with an ultrasonic meter that also acts as a reasonable flow conditioner.
  • meters In pipeline operations and other industrial applications, meters must be capable of accurately measuring the flow rate of gases or liquids moving through piping or tubing systems. In natural gas pipelines, for example, these flow rate measurements may be relied upon for custody transfer, leak detection, control, or for other indications.
  • the meter is the point where custody transfer occurs, such as when gas is delivered into or out of a pipeline system through the meter as it measures the passing flow rate.
  • the volume of gas that passes through the meter can be determined, and a custody transfer volume ticket can then be prepared.
  • the pipeline transportation fee is based on the volume of product moved through the system, i.e. the custody transfer volume.
  • a custody transfer metering system is commonly referred to in the pipeline industry as the “cash register,” and pipeline operators take great care to maintain its measurement accuracy.
  • Measurement systems comprising two or more meters may perform a pipeline leak detection function.
  • a pipeline typically operates in a “packed” or full-line condition. Therefore, as gas is pumped into the system through the inlet meter, gas is simultaneously delivered out of the system through the outlet meter, and the measurements taken at each meter are compared.
  • This “meter-in, meter-out” approach provides two modes of leak detection. First, the flow rate measured by the inlet meter should match the flow rate measured by the outlet meter within a certain accuracy tolerance, taking into account characteristics that may cause flow rate deviations, such as elevation differences or product temperature variations. Second, by measuring flow rate over a given time period, the volume moved through each meter can be determined, and the inlet and outlet meter volume measurements should correlate over that time period.
  • a measurement discrepancy could indicate a pipeline leak, although the storage of gas in the pipeline (line packing) makes short-term leak measurements difficult. Nonetheless, early leak detection enables a pipeline operator to locate and repair the problem more quickly, thereby minimizing the environmental and public safety impacts of a leak. Thus, accurate metering systems are necessary for profitable, safe, and reliable pipeline system operations and other industrial applications.
  • Flow meters are available in many different forms. Most conventional meters, such as turbine meters, are inserted directly into the flow stream where the gas drives a rotor mounted within a meter housing. The meter measures the number of rotations per unit time, which is proportional to the gas flow rate. These meters are fairly expensive and require regular calibrations to maintain accuracy over a long time period. They are also intrusive to the flow stream and include moving parts with close internal tolerances that are susceptible to damage from gas flow stream contaminants.
  • the ultrasonic meter is often a preferable metering device in gas flow streams because it overcomes the problems of conventional in-line meters by measuring flow rate in a non-invasive fashion, with considerable accuracy, and with no moving parts.
  • An ultrasonic meter includes two or more transducers that emit ultrasonic waves into the flow stream and measure the propagation time of each wave to determine the flow rate of the passing gas stream.
  • An ultrasonic wave is a sound wave having a frequency above the audible sound range, and more particularly, having a frequency >20 kHz.
  • a typical ultrasonic meter emits ultrasonic waves at frequencies between 50 kHz and 300 kHz, and preferably between 80 kHz and 180 kHz.
  • U.S. Pat. No. 4,646,575 (hereby incorporated herein by reference for all purposes) discloses an ultrasonic meter and many of its features.
  • An ultrasonic measurement system may include a silencer placed between the meter and other equipment in the measurement flow stream.
  • the silencer reduces stray ultrasonic noise that interferes with the accuracy of the ultrasonic meter. Such stray ultrasonic noise is commonly produced during gas distribution where the gas pressure is dropped precipitously and generates substantial noise (i.e. enough to interfere with measurements).
  • a pressure-regulating valve that reduces the pressure of multiple incoming flow streams as the gas is combined into a common supply pipeline, or reduces the pressure from a main supply grid to local distribution, is another source of ultrasonic noise.
  • Environmental regulations set upper limits on the acoustic noise level that industrial equipment can emit.
  • a pressure-regulating valve may be designed, for example, to reduce gas pressure by variably restricting small holes drilled into a rigid steel plate to reduce, as far as possible, the emission of sound waves in the acoustic range of frequencies.
  • the pressure regulating valve instead generates high levels of broad band ultrasonic noise. This ultrasonic noise propagates through the gas to interfere with the ultrasonic flow meter signals, resulting in a poor signal to noise ratio and a loss of measurement accuracy.
  • Silencers are designed to attenuate the wave energy of stray ultrasonic noise by reflection, absorption or both.
  • PCT Application WO 97/31365 discloses one type of ultrasonic silencer that uses a diffuser arrangement, such as a perforated tubular body, with a multiplicity of small-area surfaces that frequently reflect the ultrasonic waves. These reflections result in destructive interference between the acoustic paths, thereby effectively damping the ultrasonic noise.
  • the noise is attenuated by scattering the ultrasonic energy from the wave and reflecting it in many different directions.
  • the diffuser surfaces of the silencer are preferably at least partially curved, leading to the formation of vortices inside the gas flow that likewise cause acoustic path interference to reduce the ultrasonic noise.
  • These gas vortices can introduce undesirable flow disturbances into the measurement path, thus requiring the silencer to be located a minimum distance away from the meter. This distance requirement may be undesirable when space is limited.
  • a second type of silencer relies on absorption to attenuate stray ultrasonic noise.
  • This silencer is a foam plug, formed of an open-cell material that is inserted into the flow stream for the gas to pass through before entering the measurement flow path.
  • the foam plug attenuates noise by converting the ultrasonic energy into thermal energy through friction loss in the interstices of the material.
  • high-pressure loss is observed as the gas flows through the foam plug.
  • the foam plug acts to filter dirt and absorb liquids in the flow stream.
  • the open-cell foam plug silencer is only suitable for use in clean gas service and in systems that can accommodate high pressure loss through the silencer.
  • French Publication No. 2,737,564 discloses another type of silencer that relies on both absorption and reflection to attenuate stray ultrasonic noise.
  • This type of silencer includes a chamber with walls formed of a closed-cell, visco-elastic, absorbing material that is porous, such as, for example, a polyurethane foam, with a pore size chosen to absorb the unwanted ultrasonic waves at a particular frequency to achieve the desired attenuating effect.
  • the absorbing material may be flexible or rigid.
  • the silencer may include projecting walls that form passages to trap the ultrasonic waves, forcing multiple reflections and energy loss (by absorption) upon each reflection.
  • Another way to attenuate the ultrasonic waves by reflection is to place an obstacle, formed of either absorbing or reflecting material, internally of the chamber between the inlet and outlet of the meter. The obstacle splits the flow stream and forces the waves to be reflected many times as the waves move between the chamber inlet and outlet.
  • Silencers of this type are effective for use with ultrasonic flow meters operating at essentially atmospheric pressures of approximately 1 bar.
  • a closed cell, visco-elastic foam exhibits an acoustic performance that decreases with increasing pressure. Namely, these closed-cell foam materials do not perform well at high pressures (up to 400 bar) because they tend to compress, thereby reducing the thickness and void fraction of the material to significantly reduce the sound absorbing quality of the foam.
  • an ultrasonic silencer to be comprised of an absorbing material capable of maintaining its absorbing characteristics under high pressure operating conditions up to 400 bar. Further, it would be advantageous to have an ultrasonic silencer configured to introduce only a low pressure drop to the system. Additionally, it would be desirable to have an ultrasonic silencer that is suitable for use in either clean or contaminated gas service. It would also be desirable to have an ultrasonic silencer that introduces no flow disturbances, such as vortices, into the measurement path, but rather acts as a reasonable flow conditioner, thereby allowing the silencer to be bolted directly to the meter to minimize equipment space requirements.
  • the present invention features a silencer for use with an ultrasonic meter to reduce ultrasonic noise that would otherwise interfere with the meter and cause measurement inaccuracies.
  • the silencer should be mounted between the noise source and the ultrasonic meter.
  • the noise source may be mounted either upstream or downstream of the meter.
  • it also acts as a reasonable flow conditioner. It therefore can be mounted directly to the meter in either an upstream or downstream position without introducing flow disturbances into the measurement flow path.
  • the silencer comprises a tubular body having at least two partitioning members or baffles internally disposed therein, with the width of each baffle disposed perpendicular to the flow and the length of each baffle disposed parallel to the flow.
  • the baffles are formed of an open-cell material designed to absorb noise in the ultrasonic range of frequencies under high-pressure operating conditions, and even more preferably the baffles are formed of a reticulated metal foam.
  • the baffles are flat plate members, or in another embodiment, concentric cylindrical members, or in yet another embodiment, corrugated plate members, spaced apart one from another to partition the flow area into discrete passageways. As ultrasonic noise waves enter the silencer, the waves propagate through the flow passageways and reflect between the baffles. With each reflection, the a small quantity of ultrasonic wave energy is absorbed by the baffle material, thereby attenuating the ultrasonic noise level.
  • embodiments of the present invention comprise a combination of features and advantages that enable it to overcome various problems of prior silencers.
  • the various characteristics described above, as well as other features, will be readily apparent to those skilled in the art upon reading the following detailed description of the preferred embodiments of the invention, and by referring to the accompanying drawings.
  • FIG. 1 is a schematic illustration of an ultrasonic flow meter placed upstream of a pressure-regulating valve with the silencer of the present invention placed therebetween;
  • FIG. 2 is a schematic illustration of an ultrasonic flow meter placed downstream of a pressure-regulating valve with the silencer of the present invention placed therebetween;
  • FIG. 3 is a schematic illustration of an ultrasonic flow meter placed downstream of a pressure-regulating valve, and at an angle to the valve, with the silencer of the present invention placed at a blind-T location therebetween;
  • FIG. 4 is a schematic illustration of an ultrasonic flow meter placed upstream of a pressure-regulating valve, and at an angle to the valve, with the silencer of the present invention placed at a blind-T location therebetween;
  • FIG. 5 is an end view of a silencer according to one embodiment of the present invention, incorporating a plurality of parallel, flat plate partitioning members or baffles having open spaces or passageways therebetween;
  • FIG. 6 is a cross-sectional view of the silencer illustrated in FIG. 5 taken along the section line 6 — 6 ;
  • FIG. 7 is a graph used for designing various silencer dimensions, assuming the silencer has a 50% open configuration
  • FIG. 8 is a graph used for designing various silencer dimensions, assuming the silencer has a 66% open configuration
  • FIG. 9 is an end view of a silencer according to another embodiment of the present invention, incorporating a plurality of concentric, cylindrical partitioning members or baffles having open spaces or passageways therebetween;
  • FIG. 10 is a perspective view of the silencer illustrated in FIG. 9;
  • FIG. 11 is an end view of a silencer according to yet another embodiment of the present invention incorporating a plurality of parallel, corrugated plate baffles having open spaces or passageways therebetween;
  • FIG. 12 is a perspective view of the silencer illustrated in FIG. 11 .
  • FIGS. 1 through 4 show relative arrangements of an ultrasonic meter (USM) 10 , a pressure-regulating or flow-control valve (FCV) 20 , and a silencer (SIL) 100 .
  • the arrows represent flow through a pipe with the arrowheads pointing toward the direction of flow.
  • the term “upstream” will be used to indicate a position away from the direction of flow
  • the term “downstream” will be used to indicate a position toward the direction of flow.
  • the ultrasonic meter 10 is positioned upstream of the silencer 100
  • the flow-control valve 20 is positioned downstream of the silencer 100
  • the meter 10 is positioned downstream of the silencer 100
  • the valve 20 is positioned upstream of the silencer 100 .
  • FIG. 1 and FIG. 2 schematically depict the preferred location of a silencer 100 within a straight section of pipe relative to an ultrasonic meter 10 and equipment that generates stray ultrasonic noise, such as, for example, a pressure-regulating valve or flow-control valve 20 .
  • the silencer 100 preferably is positioned between the ultrasonic meter 10 and the flow-control valve 20 to reduce the level of stray ultrasonic noise that the valve 20 generates as it opens and closes. In this way, the silencer 100 prevents the ultrasonic noise from interfering with the ultrasonic signals of the meter 10 . Without the silencer 100 , such interference could significantly impact measurement accuracy.
  • the silencer 100 of the present invention has experimentally been shown to act as a reasonable flow conditioner, thereby smoothing out the flow instead of introducing flow disturbances.
  • the silencer 100 of the present invention may be positioned at any point along the pipe section between the flow-control valve 20 and the ultrasonic meter 10 , including directly adjacent the meter 10 . Eliminating the conventional minimum separation distance between the silencer 100 and the meter 10 is especially advantageous where space is limited, such as in offshore installations.
  • FIG. 3 and FIG. 4 schematically depict the preferred position of a silencer 100 relative to an ultrasonic meter 10 and a flow-control valve 20 that are separated by an angle, such as, for example, a 90-degree angle.
  • FIG. 3 shows the relative positions when the flow-control valve 20 is upstream of the meter 10
  • FIG. 4 shows the relative positions when the flow-control valve 20 is downstream of the meter 10 .
  • the silencer 100 should again be located between the meter 10 and the valve 20 , and in a linear relationship with the valve 20 , so that the ultrasonic noise waves emanating from the valve 20 will impinge on the silencer 100 .
  • the silencer is typically mounted at a blind-T location, and the entrance to the silencer is physically positioned at the corner 15 where the pipe changes direction to make the angle.
  • FIG. 5 and FIG. 6 depict one embodiment of the silencer 500 of the present invention.
  • FIG. 5 is a representative end view of the silencer 500
  • FIG. 6 is a cross-sectional view of the silencer 500 taken along section line 6 — 6 of FIG. 5 .
  • the silencer 500 includes a tubular body 510 , a plurality of flat, plate partitioning members or baffles 520 , 530 , 540 forming flow spaces or passageways 515 , 525 , 535 , 545 therebetween, and at least one support fixture 550 .
  • the diameter T of the tubular body 510 is commonly sized to match the diameter of the pipe section within which the silencer 500 is disposed. However, the diameter T of the tubular body 510 may be larger or smaller than the surrounding pipe section, depending upon the particular installation.
  • the tubular body 510 may have flanged ends 512 , 514 for a bolted connection to flanges mounted on the pipe section, or the ends 512 , 514 may be tapered for welding into the pipe section, or threaded for threaded connection, or the ends 512 , 514 may have any other suitable configuration for connecting to the pipe.
  • the silencer 500 includes at least two internal partitioning members or baffles, such as the three baffles 520 , 530 , 540 depicted in FIGS. 5 and 6. Of course, many more baffles may be included depending on design criteria, such as baffle width and the spacing between the baffles as explained below.
  • Baffles 520 , 530 , 540 are formed of an open-cell material designed to absorb ultrasonic noise and withstand high flow rates and high pressure operating conditions up to approximately 400 bar.
  • Baffles 520 , 530 , 540 may be made from an open-cell, visco-elastic material, but it is particularly preferred that they be made from a reticulated metal foam material, and more preferably Retimet® metal foam, manufactured by Dunlop Limited Aviation Division.
  • the baffles may be made from a closed-cell material, but the disclosed silencers have been particularly designed to withstand high pressure environments, and thus the closed-cell materials are not preferred.
  • the baffles 520 , 530 , 540 are generally the same size, each having a width D and a length L, and they are spaced apart to partition the flow area into discrete flow spaces or passageways 515 , 525 , 535 , 545 through which the gas flows between the baffles 520 , 530 , 540 .
  • the flow spaces 515 , 525 , 535 , 545 are generally the same size, each having a gap dimension H.
  • the quantity of baffles, the width D, the length L, and the gap between baffles H are all determined based on the pipe size, flow conditions, and the level of ultrasonic noise reduction required. As shown, the length L of the baffles is typically the same as the tubular body 510 , but this is not necessary to the invention.
  • At least one support fixture 550 is provided, and more than one may be provided at interval S along the length L of the silencer 500 (i.e. baffles 520 , 530 , 540 ).
  • the support fixture 550 connects between and maintains the position of the baffles 520 , 530 , 540 within tubular body 510 such that flow spaces 515 , 525 , 535 , 545 are provided, each having gap dimension H.
  • the support fixture 550 may connect spacing blocks 560 between the baffles 520 , 530 , 540 to maintain the gap H, or washers 570 may be provided to position the baffles 520 , 530 , 540 along the support fixture 550 , or alternatively the support fixture 550 may include notches 580 to position the baffles 520 , 530 , 540 along its length.
  • the support fixture 550 may be a bolt, a section of metal, or any structure that is sufficiently rigid to withstand high pressure and high flow rate operating conditions.
  • a single support fixture 550 may pass radially at any angle through the tubular body 510 and baffles 520 , 530 , 540 , such as top-to-bottom through the centerline as shown in FIG.
  • support fixture 550 may be provided at interval S.
  • the quantity of support fixtures 550 , the radial angle of the support fixtures 550 with respect to the tubular body 510 , and the interval S are adjustable based on the flow conditions.
  • the support fixture 550 connects, such as by threads or by welding, to the tubular body 510 at 552 , 554 .
  • the purpose of support fixture 550 is to lend support and stability to the baffles so that they maintain their position and spacing. Support fixture 550 may also help the baffles keep their shape and integrity in high velocity gas flows.
  • the silencer 500 attenuates the level of ultrasonic stray noise by absorption.
  • the ultrasonic noise waves move in the flow spaces 515 , 525 , 535 , 545 , reflecting between the baffles 520 , 530 , 540 and along their length L.
  • the configuration of the baffles 520 , 530 , 540 encourages a multiplicity of reflections, and with each reflection, the material that forms the baffles 520 , 530 , 540 absorbs a small amount of energy that is lost by friction in the pores or interstices of the foam material.
  • the noise absorbing capacity of a foam material is based on whether the material is impedance-matched with the gas.
  • the acoustic impedance Z of a material is defined as:
  • the open-cell nature of the reticulated metal foam material forming the baffles 520 , 530 , 540 makes the silencer 500 suitable for use in high pressure operating conditions.
  • the pore spaces within the material allow pressure internally of the baffles 520 , 530 , 540 to equalize with the external pressure. Therefore, the material forming the baffles 520 , 530 , 540 maintains its absorbing capability and does not tend to crush under high pressures.
  • the design and performance of the silencer 500 is based on selecting the diameter T of the tubular body 510 , the grade of reticulated metal foam material that forms the baffles 520 , 530 , 540 , the width D and the length L of the baffles 520 , 530 , 540 , and the gap dimension H of the flow spaces 515 , 525 , 535 , 545 . To determine these parameters, the flow rate, pressure drop, contaminants in the flow stream, and the required ultrasonic noise reduction are all considered, and a compromise is made to determine the best combination of variables for the given application.
  • the diameter T of the tubular body 510 is selected to match the diameter of the pipe, and the diameter of the pipe is determined based on the anticipated high flow rate of the gas in the system. For example, given an expected high gas flow rate, the pipe diameter may be sized to provide a flow velocity of 20 meters per second, and the diameter T of the tubular body 510 will typically be sized to match the pipe.
  • the ultrasonic noise wavelength ⁇ and the contaminants in the gas flow stream are the primary considerations when selecting the reticulated metal foam material forming the baffles 520 , 530 , 540 .
  • the wavelength ⁇ of the ultrasonic noise is given by:
  • the grade with the highest quantity of pores per inch, i.e. grade 80, will provide the greatest noise reduction because when the pores are small relative to the wavelength of the ultrasonic noise, the baffles 520 , 530 , 540 will absorb a greater amount of energy by friction with each reflection. However, liquid or solid contaminants in the gas flow stream will tend to fill and clog the pores in the metal foam material, thereby reducing its effectiveness.
  • the velocity of the gas flow may be reduced by use of a tubular body 510 with a larger diameter T than the pipeline diameter. However, this may affect the flow conditioning performance of the design.
  • the gap H should be larger than the width D.
  • the baffle width D must be wide enough to be “visible” to the ultrasonic noise wave, i.e. to be an obstacle to its path. If the baffle width D is too narrow, the wave will simply pass through it and will not be reflected. Therefore, D should be dimensioned to be at least one wavelength ⁇ .
  • a 40 dB reduction in ultrasonic noise levels (i.e. 99% reduction in amplitude) will be achieved by following these guidelines and having a length L for the baffles of 100 ⁇ to 200 ⁇ .
  • a length of 600 mm will ensure a noise reduction of 40 dB.
  • a length of about 200 mm (i.e. from 100 mm to 300 mm) is generally preferred.
  • FIG. 7 and FIG. 8 are derived from a numerical model and can be useful for determining the gap dimension H and the baffle length L for a given silencer 500 configuration.
  • FIG. 7 assumes a 50% open baffle configuration
  • FIG. 8 assumes a 66% open baffle configuration.
  • the 50% open configuration, where H ⁇ D encourages more reflections than the 66% open configuration and therefore provides more effective noise reduction, allowing for a comparatively shorter baffle length L to accomplish the same overall noise attenuation.
  • This configuration may be preferable where space is limited, but an increase in noise reduction performance typically results in higher pressure drop across the silencer 500 .
  • the 66% open configuration may be preferable, therefore, where space is not critical, but limiting pressure drop through the silencer 500 is important.
  • the graph shown in FIG. 7 includes a quantity ⁇ along the lower X-axis, defined as:
  • the total length L of the baffles can be determined based on the following formula for L L , the total attenuation loss across the silencer 500 :
  • the total attenuation loss L L required for the particular installation is input as a known quantity into the equation, and the values for L h and H are also known, so L can be calculated.
  • the total attenuation loss L L required for a particular installation is 40 dB
  • the gap H should normally be greater than the width D to prevent the silencer 500 from generating self-noise.
  • FIG. 7 and FIG. 8 assume configurations that are 50% open and 66% open respectively, giving some guidance as to the dimension of width D relative to the gap H.
  • Retimet® grade 45 is commercially available in 2 mm, 4 mm, 7 mm and 13 mm widths.
  • the total pressure drop ⁇ P T through the silencer 500 is provided as follows:
  • K ENTRANCE , K EXIT , K FRICTION entrance, exit and friction losses
  • pressure losses K are defined by:
  • FIG. 9 and FIG. 10 depict another embodiment of the silencer 800 of the present invention.
  • FIG. 9 is a representative end view of the silencer 800
  • FIG. 10 is a perspective view of the silencer 800 of FIG. 9 .
  • the silencer 800 includes a tubular body 810 , a plurality of concentric, cylindrical baffles 820 , 830 , 840 having flow spaces or passageways 815 , 825 , 835 , 845 therebetween, and at least one support fixture 850 .
  • the tubular body 810 has a diameter T 1 that typically matches the diameter of the pipe section within which the silencer 800 is disposed.
  • the tubular body 810 may have flanged ends 812 , 814 for a bolted connection to flanges mounted on the pipe section, or the ends 812 , 814 may have any other suitable configuration for connecting to the pipe.
  • the silencer 800 includes at least two, and more commonly a plurality of baffles, such as three baffle; 820 , 830 , 840 as depicted in FIGS. 9 and 10.
  • the baffles 820 , 830 , 840 are formed of an open-cell material that is preferably a reticulated metal foam material, and more preferably Retimet® metal foam.
  • the baffles 820 , 830 , 840 each have a comparable wall thickness D 1 and a comparable length L 1 , and they are spaced apart by flow spaces 815 , 825 , 835 , 845 through which the gas flows between the baffles 820 , 830 , 840 .
  • the flow spaces 815 , 825 , 835 , 845 are generally the same size, each having a gap dimension H 1 .
  • At least one support fixture 850 is provided to maintain the position of the baffles 820 , 830 , 840 within tubular body 810 .
  • a single support fixture 850 may pass radially at any angle through the tubular body 810 and baffles 820 , 830 , 840 , such as top-to-bottom through the centerline as shown in FIG. 9 .
  • more than one support fixture 850 may be provided.
  • the support fixtures 850 connect, such as by threads or by welding, to the tubular body 810 at 852 , 854 .
  • the operating considerations and calculations used to design the silencer 500 of FIGS. 5 and 6 would also apply to the silencer 800 of FIGS. 9 and 10.
  • the two-dimensional L h curves provided in FIG. 7 and FIG. 8 can be applied to the axi-symmetric silencer 800 configuration.
  • the same procedure would be followed to determine the silencer 800 baffle wall thickness D 1 , the gap H 1 , and the baffle length L 1 depicted in FIGS. 9 and 10.
  • FIG. 11 and FIG. 12 depict yet another embodiment of the silencer 900 of the present invention.
  • FIG. 11 is a representative end view of the silencer 900
  • FIG. 12 is a perspective view of the silencer 900 of FIG. 11 .
  • the silencer 900 includes a tubular body 910 , a plurality of corrugated, plate baffles 920 , 930 , 940 having flow spaces or passageways 915 , 925 , 935 , 945 therebetween, and at least one support fixture 950 .
  • the tubular body 910 has a diameter T 2 that typically matches the diameter of the pipe section within which the silencer 900 is disposed.
  • the tubular body 910 has ends 912 , 914 that may be flanged or ends 912 , 914 may have any other suitable configuration for connecting to the pipe.
  • the silencer 900 includes at least two, and more commonly a plurality of baffles, such as three baffles 920 , 930 , 940 as depicted in FIGS. 11 and 12, and the baffles 920 , 930 , 940 are preferably formed of Retimet® metal foam.
  • the baffles 920 , 930 , 940 each have approximately the same width D 2 and length L 2 , and they are spaced apart by flow spaces 915 , 925 , 935 , 945 through which the gas flow passes between the baffles 920 , 930 , 940 .
  • the flow spaces 915 , 925 , 935 , 945 are generally the same size, each having a gap dimension H 2 .
  • At least one support fixture 950 is provided and connects to the tubular body 910 at 952 , 954 .
  • the operating considerations and the calculations used to design the silencer 500 of FIGS. 5 and 6 also apply to the silencer 900 of FIGS. 11 and 12.
  • the L h curves of FIG. 7 and FIG. 8 can be applied to the silencer 900 configuration.
  • the same procedure would be followed to determine the silencer 900 baffle wall thickness D 2 , the gap H 2 , and the baffle length L 2 depicted in FIGS. 11 and 12.
  • the silencer performance for a specific measurement application is defined by the grade of material that forms the baffles, the diameter of the tubular body, the width and length dimensions of the baffles, and the gap between baffles. These parameters are determined based on a compromise between: 1) achieving the desired reduction in ultrasonic noise level, 2) limiting the pressure drop through the silencer to acceptable levels, 3) achieving the lengthwise spacing requirements of the particular installation, and 4) ensuring the gas flow through the silencer remains below about a tenth of the sonic velocity to prevent the silencer from generating self-noise in the acoustic range of frequencies.

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  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Pipe Accessories (AREA)
  • Measurement Of Mechanical Vibrations Or Ultrasonic Waves (AREA)
  • Measuring Volume Flow (AREA)
  • Transducers For Ultrasonic Waves (AREA)
US09/740,427 2000-12-19 2000-12-19 Noise silencer and method for use with an ultrasonic meter Expired - Fee Related US6533065B2 (en)

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US09/740,427 US6533065B2 (en) 2000-12-19 2000-12-19 Noise silencer and method for use with an ultrasonic meter
EP01310488A EP1217339A3 (fr) 2000-12-19 2001-12-14 Amortisseur de bruit et méthode pouré utiliser avec un débitmètre à ultrasons
CA002365051A CA2365051A1 (fr) 2000-12-19 2001-12-17 Silencieux et methode connexe pour utilisation avec un appareil de mesure aux ultrasons
MXPA01013102A MXPA01013102A (es) 2000-12-19 2001-12-18 Silenciador de ruido y metodo para el uso con un medidor ultrasonico.
RU2001134205/28A RU2001134205A (ru) 2000-12-19 2001-12-19 Шумоподавитель и способ снижения уровня помех в ультразвуковом диапазоне частот, измерительная система с шумоподавлением и способ конструирования шумоподавителя

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US20050112397A1 (en) * 2003-07-24 2005-05-26 Rolfe Jonathan L. Assembled non-random foams
US20050193832A1 (en) * 2003-02-10 2005-09-08 Tombs Michael S. Multi-phase Coriolis flowmeter
US20050205147A1 (en) * 2004-03-18 2005-09-22 Sawchuk Blaine D Silencer for perforated plate flow conditioner
US7059199B2 (en) 2003-02-10 2006-06-13 Invensys Systems, Inc. Multiphase Coriolis flowmeter
US20060124385A1 (en) * 2004-12-10 2006-06-15 Ingersoll-Rand Company Modular pressure pulsation dampener
US20060272886A1 (en) * 2005-06-07 2006-12-07 Christian Mueller Silencer
US20070045044A1 (en) * 2005-08-26 2007-03-01 Sullivan John T Flow-through mufflers with optional thermo-electric, sound cancellation, and tuning capabilities
US20070277530A1 (en) * 2006-05-31 2007-12-06 Constantin Alexandru Dinu Inlet flow conditioner for gas turbine engine fuel nozzle
US20080128199A1 (en) * 2006-11-30 2008-06-05 B&C Speakers S.P.A. Acoustic waveguide and electroacoustic system incorporating same
US20080246277A1 (en) * 2007-04-04 2008-10-09 Savant Measurement Corporation Multiple material piping component
US20090050404A1 (en) * 2005-03-18 2009-02-26 Ralf Corin Sound Dampening Flow Channel Device
DE102007048881A1 (de) 2007-10-11 2009-04-16 Siemens Ag Massendurchflussmessgerät sowie Verfahren zur Herstellung eines Versteifungsrahmens für ein Massendurchflussmessgerät
US20100251701A1 (en) * 2007-11-12 2010-10-07 Impulse Engine Technology Pty Limited Muffler
US8950188B2 (en) 2011-09-09 2015-02-10 General Electric Company Turning guide for combustion fuel nozzle in gas turbine and method to turn fuel flow entering combustion chamber
US10065212B2 (en) 2015-09-04 2018-09-04 Motorola Solutions, Inc. Ultrasonic transmitter
US10228351B2 (en) 2014-09-24 2019-03-12 Rosemount Inc. Acoustic detection in process environments
US10976295B2 (en) 2017-06-26 2021-04-13 Mustang Sampling Llc System and methods for methane number generation

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FI117648B (fi) 2004-03-02 2006-12-29 Jeven Oy Ilmavirtauksen säätö- ja vaimennuslaite
WO2008028846A1 (fr) * 2006-09-04 2008-03-13 Steinway & Sons Procédé d'amélioration du son d'un instrument
DE102008049891B4 (de) * 2008-10-02 2012-12-06 Hydrometer Gmbh Strömungsrichter für ein Durchflussmessgerät, insbesondere ein Ultraschallmessgerät
JP6209732B2 (ja) * 2013-05-29 2017-10-11 パナソニックＩｐマネジメント株式会社 超音波流量計測装置
WO2017048848A1 (fr) * 2015-09-14 2017-03-23 Michael Mullin Système de débitmètre
US10655990B1 (en) 2016-05-06 2020-05-19 Big Elk Energy Systems, LLC In-line ultrasonic attenuation end treatment for use with an ultrasonic gas flow meter
CN107503822B (zh) * 2017-09-21 2023-12-01 重庆广亚机械制造有限公司 一种汽车排气消音器
AU2020250998A1 (en) * 2019-03-29 2021-10-28 Fisher & Paykel Healthcare Limited Muffler
CN112813933A (zh) * 2021-01-20 2021-05-18 福建水利电力职业技术学院 一种隐形式消音消能消力戽
CN116499781B (zh) * 2022-05-20 2024-05-17 连云港观旭电力节能设备有限公司 一种消音器测试方法、系统、装置及介质

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US7303046B2 (en) 2002-09-18 2007-12-04 Savant Measurement Corporation Apparatus for filtering ultrasonic noise within a fluid flow system
US20040055816A1 (en) * 2002-09-18 2004-03-25 Gallagher James E. System, apparatus, and method for filtering ultrasonic noise within a fluid flow system
US7303048B2 (en) * 2002-09-18 2007-12-04 Savant Measurement Corporation Method for filtering ultrasonic noise within a fluid flow system
US7303047B2 (en) * 2002-09-18 2007-12-04 Savant Measurement Corporation Apparatus for filtering ultrasonic noise within a fluid flow system
US20060011413A1 (en) * 2002-09-18 2006-01-19 Savant Measurement Corporation Method for filtering ultrasonic noise within a fluid flow system
US7011180B2 (en) * 2002-09-18 2006-03-14 Savant Measurement Corporation System for filtering ultrasonic noise within a fluid flow system
US7059199B2 (en) 2003-02-10 2006-06-13 Invensys Systems, Inc. Multiphase Coriolis flowmeter
US20080034892A1 (en) * 2003-02-10 2008-02-14 Invensys Systems, Inc. Multi-phase coriolis flowmeter
US7698954B2 (en) 2003-02-10 2010-04-20 Invensys Systems, Inc. Multi-phase Coriolis flowmeter
US20060161366A1 (en) * 2003-02-10 2006-07-20 Invensys Systems, Inc. Multiphase coriolis flowmeter
US20110016988A1 (en) * 2003-02-10 2011-01-27 Invensys Systems, Inc. Multi-phase coriolis flowmeter
US8117921B2 (en) 2003-02-10 2012-02-21 Tombs Michael S Multi-phase coriolis flowmeter
US7188534B2 (en) 2003-02-10 2007-03-13 Invensys Systems, Inc. Multi-phase coriolis flowmeter
US7207229B2 (en) 2003-02-10 2007-04-24 Invensys Systems, Inc. Multiphase Coriolis flowmeter
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US20050112397A1 (en) * 2003-07-24 2005-05-26 Rolfe Jonathan L. Assembled non-random foams
US20050205147A1 (en) * 2004-03-18 2005-09-22 Sawchuk Blaine D Silencer for perforated plate flow conditioner
US7073534B2 (en) 2004-03-18 2006-07-11 Blaine Darren Sawchuk Silencer for perforated plate flow conditioner
US20060124385A1 (en) * 2004-12-10 2006-06-15 Ingersoll-Rand Company Modular pressure pulsation dampener
US8061476B2 (en) * 2005-03-18 2011-11-22 Tumane Enterprises Limited Sound dampening flow channel device
US20090050404A1 (en) * 2005-03-18 2009-02-26 Ralf Corin Sound Dampening Flow Channel Device
US20060272886A1 (en) * 2005-06-07 2006-12-07 Christian Mueller Silencer
US20070045044A1 (en) * 2005-08-26 2007-03-01 Sullivan John T Flow-through mufflers with optional thermo-electric, sound cancellation, and tuning capabilities
US7610993B2 (en) * 2005-08-26 2009-11-03 John Timothy Sullivan Flow-through mufflers with optional thermo-electric, sound cancellation, and tuning capabilities
US20070277530A1 (en) * 2006-05-31 2007-12-06 Constantin Alexandru Dinu Inlet flow conditioner for gas turbine engine fuel nozzle
US20080128199A1 (en) * 2006-11-30 2008-06-05 B&C Speakers S.P.A. Acoustic waveguide and electroacoustic system incorporating same
US7845688B2 (en) 2007-04-04 2010-12-07 Savant Measurement Corporation Multiple material piping component
US20080246277A1 (en) * 2007-04-04 2008-10-09 Savant Measurement Corporation Multiple material piping component
DE102007048881A1 (de) 2007-10-11 2009-04-16 Siemens Ag Massendurchflussmessgerät sowie Verfahren zur Herstellung eines Versteifungsrahmens für ein Massendurchflussmessgerät
US20100251701A1 (en) * 2007-11-12 2010-10-07 Impulse Engine Technology Pty Limited Muffler
US8950188B2 (en) 2011-09-09 2015-02-10 General Electric Company Turning guide for combustion fuel nozzle in gas turbine and method to turn fuel flow entering combustion chamber
US10228351B2 (en) 2014-09-24 2019-03-12 Rosemount Inc. Acoustic detection in process environments
US10065212B2 (en) 2015-09-04 2018-09-04 Motorola Solutions, Inc. Ultrasonic transmitter
US10976295B2 (en) 2017-06-26 2021-04-13 Mustang Sampling Llc System and methods for methane number generation

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US20030034202A1 (en) 2003-02-20
EP1217339A3 (fr) 2003-05-28
CA2365051A1 (fr) 2002-06-19
MXPA01013102A (es) 2004-05-21
EP1217339A2 (fr) 2002-06-26
RU2001134205A (ru) 2003-09-10

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